In-feed mechanism



Sept. 10, 1968 1.; lvERsl-:N

. IN-FEED MECHANISM Filed April ll, 1966 -6 Sheets-Sheet 5 .Larenz lversen H/.S' ATTORNE YS Sept. 10, 1968 lvERsL-:N 3400,496

IN-FEED MEcHANIsM Filed April ll. 1966 6 Sheets-Sheet 4 HIS TTORNE YS Sept. 10, 1968 lvl-:RSEN

IN-FEED MECHANISM e Sheets-Sheet 5 Filed April ll, 1966 HIS ATTORNEYS Sept. 10, 1968 L. lvERsEN 3400496 IN-FEED MECHANISM Filed April ll, 1966 6 Sheets-Sheet 6 INVENTOR. L Lorenz /versen HIS A TTORNEYS 3,400,496 IN-FEED MECHANISM Lorenz Iversen, Pittsburgh, Pa., assignor to Mesta Machine Company, Pittsburgh, Pa., a corporation of Pennsylvania Filed Apr. 11, 1966, Ser. No. 541,717 .13 Claims. (Cl. 51-165) ABSTRACT OF THE DISCLOSURE I disclose, in a grinding apparatus, the combination comprising a carriage structure mounted on slideway means supported by said apparatus for movement toward and away from a workpiece when supported adjacent said apparatus, a carriage section pivotally mounted on said carriage structure adjacent the forward end thereof, a grinding wheel mounted on said carriage section but displaced from the pivotal mounting being so disposed that movements of the rearward end of said carriage section produce corresponding approach and withdrawal movements of said grinding wheel relative to said workpiece, means for moving said carriage structure along said slideway means constituting a relatively coarse feed adj ustment for said grinding wheel, a supporting link for said rearward carriage section end adjustably mounted on said apparatus, and a fine feed eccentric rotatably mounted on said carriage section rearward end and engaging said supporting link.

The present invention relates to grinding apparatus and more particularly to a device for grinding the surface of rolls for various uses such as in rolling mills, or in calendering or other machines, wherein a grinding Wheel is provided to rotate in contact with the roll to be ground, with the grinding apparatus being further arranged for an extremely fine control of its grinding wheel feeding mechanism in conjunction with the normal coarse feeding and crowning mechanisms of the grinding apparatus.

As illustrated, the roll to be ground is rotatably mounted at a stationary location, while the grinding apparatus is slidably mounted upon both transverse and approach slideways whereby the grinder can traverse the length of the roll and can be moved toward and away from the center line of the roll supports so that rolls of differing diameters can be accommodated. In addition, the grinding apparatus is usually provided with an automatic crowning mechanism which induces negative or positive feeding movements of the grinding wheel as the grinding apparatus traverses the roll in order to produce a crown or concavity, respectively, along the length of the roll.

In the operation of this form of grinding apparatus, the mechanism controlling movements of the grinding wheel and associated components of the apparatus along the approach slideways usually includes a feed screw Operating in conjunction with a threaded nut or the like carried by the approach slide, and the extremely fine adjustment thereof as required for the maintenance of close tolerances is very difficult for the average operator to make in practice. Further, almost invariably the mechanism required for this purpose inherently contains or develops looseness or play resulting in backlash. Thus, manipulation of a hand wheel or the operation of other apparatus controlling the feed screw does not accurately reflect the motion of the approach slide and with it the grinder feed.

The arrangement of my grinding apparatus overcomes these difficulties by providing a fine feed control mechanism, which is operable to the same degree irrespective United States Patent O ICC of the positional Variation of an automatic crowning control which I also provided in the aforesaid arrangement for operation in conjunction with the fine feed control. Moreover, my crowning control is made adjustable in a manner such that adjustment thereof in nowise afects the operation of my fine feed control. Furthermore, the fine feed control of my arrangement can be set manually or by a motorized operator to manipulate the same to very close tolerances throughout the Variation in feed of the grinder induced by the crowning control as the grinder is rnoved or traversed along the length of the roll.

I accomplish these desired results by providing a traverse slideway arranged generally parallel to the central axis of a roll when supported for grinding by my apparatus, a traversing carriage mounted for sliding movement along said traverse slideway and having an approach slideway mounted thereon, an approach carriage mounted for sliding movement along the approach slideway, an elongated fine feed and crowning section pivotally connected to said approach carriage adjacent the forward end thereof so that the feed section is mounted for limited pivotal movement through a Vertical or transverse arc relative to said roll, said grinding wheel being displaced from said pivot point so that Vertical pivoting movement of said feed section results in moving the grinding wheel toward and away from the roll, an eccentrically controlled crowning link supporting the other end of the feed section with the crowning link eccentric being controlled through a gear train operated by movement of the traversing carriage along the traverse slideway, and said crowning link being rotatably mounted within a fine feed eccentric which -is in turn rotatably mounted within and adjacent said other end of the pivoted feed section, together with means for moving the traversng and approach carriage along their respective slideways and for rotating the fine feed eccentric.

Additionally, I contemplate providing in my arrangement means for adjusting the height or the depth of the crown or concavity imparted to the roll in a manner which will not affect the operative engagement of the fine feed eccentric with the pivoted feed section. In one arrangement, this a'djustment means includes a hollow slideway formed within the fine feed eccentric and a crowning link rotatably and slidably mounted within the eccentric slideway and having an Operating projection loosely extending through an elongated slot formed in and extending longitudinally of the feed eccentric, with the crowning link p-rojection en'ga-ging a crowning device which is mounted for adjustable, sliding movement along a pivoted lever connected for pivotal movement to and under the contact of the aforementioned crowning eccentric. The position of the crowning link and projection along the length of the lever, along which it is moved while in sliding engagement with the fine feed eccentric thereby determines the height to which the rearward end of the feed section is raised or lowered and also the corresponding approach or the withrdrawal of the grinding wheel relative to the roll. However, despite the location of the crowning link along the length of the fine feed eccentric, and the corresponding height of depth of the crown or concavity, rotation of the fine feed eccentric vcauses the grinder to maintain the same grinding depth along the length of the roll.

These and other objects, features and advantages of the invention, together with structural details thereof, will be elaborated upon as the following description of presently preferred embodiments thereof proceeds.

In the accompanying drawings, I have shown a presently preferred embodiment of the invention wherein:

FIGURE l is a top plan view of the traversing carriage and traverse slideway of the grinding apparatus of my invention, with the approach carriage and associated components thereof having been removed in order to show the invention more clearly;

FIGURE 2 is a sectional view of the apparatus shown in FIGUR-E 1 and of the apparatus shown in FIGURE 3, taken along reference planes II- II of FIGURES 1 or 3;

FGURE 2A is an enlarged, partial view of the apparatus as shown in FIGtURE 2, and taken, therefore, along the same reference plane;

FIGURE 3 is a sectional view of the grinding apparatus shown in FIGUR'E 2 and taken generally along reference plane III-III thereof;

FGU'RE 4 is a partial sectional view of the apparatus shown in FIGURE 3 and taken along reference plane IV IV thereof;

FIGURE 5 is a side elevational view of the apparatus shown in FIGURE 3, partially in section, and taken generally along reference planes V-V of FIGURE 3 and of FIGURE 6;

FIG'URE 6 is a top plan view of the apparatus as shown in FIGURE 5 and taken generally along reference plane VI-VI thereof; and

FIGURE 7 is a partial sectional view of the apparatus shown in FIGURE 5 and taken along reference plane VII- VII thereof.

Referring now to FIGU-RE 1 of the drawings, my grinding apparatus is arranged for grinding a roll 10 which is supported on a pair of spaced end stops or centers 12, or other suitable supports 'such as conventonal journal rests. Conventional means (not shown) are provided for rotating the roll 10. A pair of traversing slideways 14 and 16 are stationarily mounted adjacent the roll end stops 12 and parallel with the center line thereof, with one of the slideways, for example, the slideway 14 being of keyed configuration as better shown in FIGIURE 2. A traversing carriage 18 having complementary slide runners 20 and 22 is mounted for reciprocal movement along the slideways 14 and 16 which complementarily engage traversing slides 20 and 22 respectively of the carriage 18.

A pair of approach slideways 24 and 26 are similarly formed on the upper surfaces of the traversing carriage 18, on which is mounted an approach carriage 28 with slides 30 and 32 thereof in engagement respectively with the approach slideways 24 and 26. If desired, suitable bearing material 34 and 36 respectively can be positioned at the areas of engagement of the aforementioned slides and slideways.

Rotatably mounted upon the carriage 18 is a shaft 39 having an approach worm 40 mounted thereon for rotation therewith. The shaft 39 extends through a longitudinal cavity 42 formed therefor in the traverse carriage 18. Suitable means (not shown) are provided for driving the shaft 39 and worm 40. The approach worm 40 when driven rotates approach worm gear 44 and in turn an approach drive screw 46 to slide the approach carriage 28 along its slideways 24 and 26. Driving connection between the drive screw 46 and the approach carriage 28 is etfected by means of threaded nut 48 engaging the drive screw 46 and secured to the underside of the approach carriage 28, for examplc, by means of mounting bolt 50. A similar drive screw (not shown) can be driven by suitable means for reciprocating the traverse carriage 18 along the traverse slideways 14 and 16.

In this arrangement of my apparatus the aforementioned approach drive screw 46 and 'associated gearing train 40, 44 together with its connection 48, 50 to the approach carriage 28 constitutes the coarse feeding mechanism for moving the grinding wheel 52 toward and away from the roll 10. For fine adjustment of the grindin g wheel 52 and associated component structures, my -grinding apparatus also includes cooperating, but independently .adjustable means for automatically imparting a crown or a concavity to the roll 10 as the traverse carriage 18 is moved prallel thereto, and for imparting a fine adjustment to the grinding wheel support 54, which fine adjustment in feed when once made will be retained irrespective of the heght or depth of the crown or concavity, if any, which is automatically imparted to the roll 10, as the grinding wheel 52 is moved therealong. Moreover, the aformentioned height or depth can be adjustably and independently varied without atfecting the setting of the fine adjustment which was previously established.

On arrangement for automatically irnparting a crown or concavity to the roll 10 includes the use of an elongated traversing rack 56 coextending with the length of the traverse slideway structure 38 and positioned adjacent and parallel to one of the traverse slideways, for example, the slideway 14, as better shown in FIGURES 2 and 3 of the drawings. A traversing pinion 58 is rotatably mounted on the undersurface of the traverse carriage 18 for clutched engagement with the traverse rack 56. In furtherance of this purpose, the traversing pinion 58 is rotatably mounted adjacent the end of a clutch lever 60 which likewise is pivoted to the underside of the traverse carriage 18 as denoted by reference Character 62. Suitable means (not shown) are provided for manipulating the other end of the lever 60, in order to raise and lower the traversing pinion 58 respectively out of or into engagement with the traverse rack 56, depending upon whether the automatic crowning mechanism of the grinding apparatus is to be employed. The rotatable mounting for the traversing pinion 58 slidably engages a slot 64 formed in the lower end portion of a crown worm shaft 66, also roatably mounted on the underside of the traverse carriage 18 as denoted by reference Character 68. The traversing pinion 58 thus is engaged with the worm shaft 66, irrespective of the elevational or clutched and unclutched position of the pinion 58.

When the clutch lever 60 is in the position as shown in FIGURE 3, the traversing pinion 58 is engatged with the rack 56 to rotate the shaft 66 and a crowning drive worm 72 also affixed to the shaft 66 for rotation therewith. The crowning drive worm 72 thus rotates crown worm gear and drive gear 74, 76 to rotate an elongated approach crowning gear 78. The elongated toothed portion 80 of the approach crowning gear 78 extcnds along the anticipated length of travel of the approach carriage 28, so that crowning eccentric gear 82 remains in enmeshment therewith despite the location of the approach carriage along its anticipated path of travel.

The gear ratios associated with the crown gearing train described thus far are selected such that the crowning eccentric gear 82 is rotated through a maximum angle of or one-half revolution when the traversing pinion 58 is moved through its maximum displacernent along the traverse rack 56, as when the longest roll within the capabilities of the grinding apparatus is positioned on the roll supports. Shorter rolls will, of course, be positioned so that their central transverse axes correspond with that of the traverse rack 56, so that the crowning eccentric gear 82 will be rotated through correspondingly lesser angles and the maximum crown height or depth of concavity will be correspondingly less.

The crowning eccentric gear 82 is secured for rotation with crowning eccentric shaft 84, which is rotatably mounted on the approach carriage 28 as denoted by reference Character 86. At the other end of the crowning eccentric shaft 84 a crown eccentric 88 is formed on which is rotatably mounted a bifurcate crowning link 90. In this example of the invention, the eccentric 8'8 is positioned on the crowning shaft 84, with relation to the crowning eccentric gear 82 and other components of the crowning gear train, so that the eccentric 88 is disposed at its lowest position, as viewed in FIGURE 2 of the drawings, when the traversing pinion 58 is disposed on the traverse rack 56 at a point coincident with the longitudinal midpoint of the work piece body, such rack being as previously stated, in the transverse control axs line of the roll 10 when the latter is positioned on roll supports. This position of the eccentric 88, as shown in FIG- URE 2, represent the maximum height of the crown imparted to the roll 10, or the point along the traversing path of the carriage 18 whereat the grinding wheel 52 iS farthest from the roll axis. This same position would represent the maximum depth of concavity, if desired, to be imparted to the roll 10, simply by rotating the eccentric 88 180 relative to its shaft 84.

As the crowning eccentric shaft revolves, the eccentric 88 and the crowning eccentric link 90', through suitable mechanical linkages presently to be described, move the grinding wheel 52 and its support 54 toward and away from the central axis of the roll 10. In furtherance of this purpose, the grinding wheel support 54 is secured to an elongated approach carriage section 92 which is pivotally mounted adjacent its forward end to the approach carriage 28 by means of a horizontal disposed pivot pin 94 and carriage brackets 96. The central axis of the grinding wheel 52 is offset from the pivot connection 94 by means of the grinding wheel support 54 so that when the rear- Ward end of the pvoted carriage section 92 is moved through a Vertical are by the crowning mechanism, the grinding wheel 52 and support 50, 54 is moved toward and away from the roll axis.

The rearward end of the pvoted carriage portion 92 is supported on and is raised and lowered by a crowning link 98 which is rotatably and slidably mounted within an elongated cavity 100 extending longitudinally, but eccentrically within a feed eccentric 102. In furtherance of this purpose, the crowning link 98 which is of generally cylindrical configuration, is rotatably mounted by means of its reduced or necke-d-down end portions 104 upon suitable anti-frictional means such as the bearings and bearing races denoted generally by reference characters 106. The outer races of the bearing structures 106 closely fit, but are slidably mounted, within the cavity 100. Thus, the feed eccentric 102 can be revolved through a limited rotative angle relative to the crowning link 98, as described in greater detail below, and for this purpose the eccentric 102 is in turn rotatably mounted within enlarged en-d portion 108 of the pvoted carriage section 92, by means of bearings 110.

For raising and lowering the crowning link 98, a crowning link projection 112 is extended through a slot 114 formed in the feed eccentric 102 and extending longitudinally thereof in communication with its cavity 100. The link 112 is rotatably mounted upon a crowning slide device 116, which in turn, is slidably mounted upon crowning adjustment lever 118, which is pvoted adjacent the midpoint thereof to the approach carriage structure 28 as denoted by reference character 120.

The purpose of the crowning lever 118, which as better shown in FIGURES 2, 2A and 4 is formed from a pair of elongated side plates 122, is to provide -an adjustment for increasing or decreasing the height of the crown imparted to the roll 10. In furtherance of this purpose, the crowning slide 116 terminates at its ends in a pair of bifurcate bracket portions 124 which slidably engage the side plates 122 respectively of the crowning lever 118. Intermediate the bifurcate portions 124, the crowning link projection 112 is rotatably mounted additionally on bearing 126 for sidewise movement to permit rotation of the projection 112 relative to the planes of the crowning lever side plates 122 in response to forward and rearward displacements of the crowning link 98 as the feed eccentric 102, in which the crowning link 98 is eccentrically mounted, is rotated.

With this arrangement, the rear end portion of the carriage section 92 is variably supported between minimum and maximum elevational limits of the crowning or supporting link 98, so that the height of the crown imparted to the roll can be adjusted from a maximum crown as denoted -by the solid outlines of the crowning link projection 112 and slide 116 in FIGURE 3 to a minimum crown as denoted by the dashed outlines 128 thereof. In furtherance of this purpose, means are provided for sliding the crowning link 98 along the length of the feed eccentric cavity 100, the length of the slot 114 of which Will accommodate the projection 112 throughout its lateral path of travel, and at the same time for moving the slide 116 along the crowning adjustment lever 118. Of course, the farther the crowning link and slide 98, 116 are moved from the fulcrum of the lever 118 as represented by its pivot point 120, the greater will be the Variation in pivotal movement of the carriage section 92 and resultantly in the displacement of the grinding 52.

One arrangement for eifecting the aforementioned sliding actions of the crowning link 98 and slide 116 includes the use of -the crowning dial and adjustment knob` denoted generally by the reference Character 130 which is secured for rotation with a shaft 132 rotatably mounted, in a Vertical position thereof, adjacent the rearward end of the pvoted approach carriage section 92. At the lower end of the crown adjustment shaft 132, a pinion 134 is secured for rotation therewith in engagement With a rack 136 suitably positioned on the adjacent side of the crowning ,link projection 112. The rack 136 is of suflicient length to permit engagement thereof with the pinion 134 throughout the path of sliding movements of the crowning link 98 and slide 116.

As noted previously, the approach drive screw 46 and related gearing train 40, 44 and other mechanical linkages constitute a relatively coarse feed adjustment for the grinding wheel 52. For fine feed adjustment, for example of the order of a mill or less, means are provided by my apparatus for correspondingly raising and lowering the rearward end of the pvoted carriage section 92 so as to produce the -desired fine-adjusting movements of the grinding wheel 52. The fine feed adjustment can 'be made independently of the position of the crowning link 98, the crown eccentric 88, and other associated components of the crowning mechanism. Moreover, the fine feed adjustment when once established operates independently to maintain the fine feed adjustment despite the positional feed Variation induced in the grinding wheel 52 by the crowning mechanism. On the other hand, the fine feed adjustment mechanism is equally operational when the crowning mechanism is disengaged as by operation of the clutch rod 60 to -disengage the traversing pinion 58 from its rack 56. Conversely, the fine feed adjustment mechanism cooperates with the crowning mechanism, when used, in -that 'a positive increment of elevation imparted, as an example, to the rearward end of the carriage section 92, as by turning the fine feed eccentric 102 through part of all of the angle defined by its slot 114, is additive algebraically to that increment of elevation introduced by the crowning link 9'8 and asso- 'ciated components at a particular position of the traverse carriage 18 along the length of the roll 10.

Thus, as better shown in FIGURE 2 of the drawings, assuming that the crowning mechanism has established a given elevation of the rearward end 108 of the pvoted carriage section 92, as defined by the relative position of the crowning eccentric 88, rotation of the fine feed eccentric 102 in the clock-Wise directon will elevate the carriage section end 108 to an extent depending upon the angle of rotation of the feed eccentric 102 within the limits defined by its slot 114. When thus positioned, of course, rotation of the eccentric 102 in the -reverse direction, to produce an angula'r displacement within the confines of the slot 114, will correspondingly lower the carriage section end 108 to produce a corresponding withdrawal of the grinding wheel 52 from -the rotational axis of the 'roll 10. It is to be understood that the slot 114 can occlude a greater or lesser rotative angle than that shown in FIGURE 2 as required in diifering applications, provided that sufiicient arcuate engagement remains between the crowning link 98 and the walls of the feed eccentric cavity to retain the crowning link within the cavity.

In order to operate the feed eccentric 102 in a controllable manner, manual 'and motor-driven means are provided for rotating the feed eccentric 102 through a prescribed angular displacement within the confines of the slot 114. As better shown in FIGURES 3 to 7, such means are cooperative with a fine feed eccentric Operating lever 138 secured as by mounting bolts 140 to the adjacent end 142 of the feed eccentric 102, which end is projected through 'an opening in the end wall of the enlarged, carriage section end 108. In this arrangement, the feed eccentric lever 138 is driven through a suitable gearing train presently to be described, which can be operated either by motor drive 144 or manually by hand wheel 146.

As better shown in FIGURE 5, both the lhand wheel 146 'and drive motor 144 are connected through suitable and known mechanical linkages to a worm shaft 148 rotatably supported within the gear housing 150. A drive worm 152 is mounted upon the shaft 148 for engagement with a worm gear 154. The worm gear 154 is pinned for rotation with 'a second rotatably mounted shaft 156 and when rotated, -operates through gearing train 158, 160, 162 to move the rack 164, to the right or to the left, as viewed in FIGURE 5 of the drawings, depending upon the rotational direction of the drive worm 152. The rack 164 is slidably mounted in a slideway 166, therefor, in the housing 150 and at its left end, as viewed in FIGURE 5, the rack 164 is pivotally connected to a link 168 which in turn is pivotally connected at its other end to the otherwise free end of the eccentric lever 138. The length of the gear portion 172 of the rack 164 is suflicent to accommodate the anticipated angular displacement of the feed eccentric lever end 170, as defined by the limits imposed by the feed eccentric slot 114.

To prevent overriding these limits when the rack 164 moved by the drive motor 144 through the aforedescribed gearing train 152-164, a pair of limit switches 174 and 176 are disposed for engagement with an operator 178 affixed to the upper side of the link 168, at the respective limits of movement of the eccentric lever 138 and the link 168 Such limit switches can be electrically connected (not shown) in the electrical circuit of the drive motor 144 to deenergize the motor 144, When the limit switches are activated. To aid in the manipulation of the feed eccentric lever 138 by manual operation of the hand wheel 146, the microswitch 174 and 176 also can be connected to energize suitable warning lamps (not shown) or other alarm indicia.

In this arrangement of my grinding apparatus, the aforedescribed gearing train 152-164 and other components thereof are dimensioned such that one revolution of the drive motor 144, by way of example, produces an incremental change of one mil in the feed approach or withdrawal, as the case may be, of the grinding wheel 52. The necessary output speed of the drive motor 144 is reduced by suitable voltage control means (not shown). In this example, the hand wheel 146 is coupled to the worm shaft 148 through a gearing unit 180 having a five-to-one ratio so that five times the aforementioned incremental feed will be induced upon one revolution of the hand wheel. To aid in the manipulation of the hand wheel 146, a suitable circumferential dial 182 is positioned concentrically with the hand wheel 146 and calibrated to read in suitable units.

From the foregoing it will be readily apparent that a novel and efiicient grinding apparatus is provided by by invention. While I have shown and described presently preferred embodiments of the invention, it is to be distinctly understood that the invention is not limited thereto but may be otherwise variously embodied within the scope of the following claims. Moreover, it `is to be understood that certain features of the invention can be advantageously utilized without a corresponding use of other features thereof.

8,4ott496 I claim:

1. In a grinding apparatus the combination comprising a carriage structure mounted on slideway means supported by said apparatus for mlo-vement toward and away from a workpiece when supported adjacent said apparatus, a carriage section pivotally mounted on said carriage structure adjacent the forward end thereof, a grinding wheel mounted on said carriage section but displaced from the pivotal mounting thereof and said pivot mounting being so disposed that movement of the rearward end of said carriage section produce corresponding approach and withdrawal movements of said grinding wheel relative to said workpiece, means for moving said carriage structure along said slideway means constituting a relatively co'arse feed adjustment for said grinding wheel, a supporting link for said rearward carriage section and adjustably mounted on said apparatus, and a fine feed eccentric rotatably mounted on said carriage section rearward end and engaging said supporting link.

2. The combination according to claim 1 wherein said slideway means includes a stationary traverse slideway structure with said carriage structure being mounted thereon and an approach slideway formed on said carriage structure and extending generally normal to said traverse slideway structure, a crowning eccentric is rotatably mounted on said carriage structure, said supporting link engages said feed eccentric and said crowning eccentric, and means are provided for rotating said crowning eccentric to move correspondingly said link and said carriage section rearward end portion and for rotating said fine feed eccentric to move said carriage section rearward end portion relative to said supporting link.

3. In a grinding apparatus, the combination comprising an elongated pivotally mounted support, a grinding wheel mounted on said support but displaced from the pivoted mounting thereof and said pivot mounting being disposed so that movements of an end portion of said support produce corresponding approach and withdrawal movements of said grinding wheel relative to a workpiece When supported adjacent said grinding Wheel, a slotted hollow fine feed eccentric rotatably mounted on said support end portion, a supporting link mounted on said apparatus adjacent said support end portion and extending through said feed eccentric slot and rotatably mounted within said feed eccentric hollow, and means for rotating said feed eccentric to move said support end portion relative to said supporting link.

4. The combination according to claim 3 wherein the width of said feed eccentric slot and the thickness of said supporting link in the region of said slot impose limits of angular displacement of said feed eccentric rotation.

5. The combination according to claim 3 wherein said feed eccentric is elongated and is mounted in said support end portion, a crowning adjustment lever is pivoted upon said apparatus and disposed generally parallel to said feed eccentric slot, said supporting link in addition is slidably mounted within said feed eccentric and slidably engages said crowning adjustment lever, a crowning eccentric rotatably is mounted adjacent said lever, a crowning eccentric link pivotally engages said crowning eccentric and said lever, and means are provided for rotating said feed eccentric and said crowning eccentric.

6. The combination according to claim 5 o haracterized in that said connecting link is pivotally mounted on said crowning adjustment lever to facilitate pivotal movement thereof and is rotatably mounted t'hereon in a direction transverse to said pivot mounting to accommodate eccentric movements of said feed eccentric.

7. The combination according to claim 3 wherein a support adjustment lever is disposed generally in the plane of said feed eccentric slot, means are provided for pivotally mounting said lever on said apparatus and adjacent said slot, said supporting link additionally is slidably mounted in said feed eccentric hollow and has its other end slidably mounted on said adjustment lever for movement therealong, and means are provided for pivotally moving said adjustment lever to support adjustably said link and said support end portion.

8. The combination according to claim 3 wherein said feed eccentric rotating means is characterized by an operating lever secured to a projecting end portion of said feed eccentric for rotation therewith, a rack linkage pivotally connected to said Operating lever, means for slidably mounting said rack linkage on said apparatus, motorized and manually driven operators fo-r said rack linkage, and a gearing train operatively engaging said rack linkage and said operators respectively.

9. The combination according to claim 7 characterized in that the pivotally moving means for said lever is a rotatably mounted crowning eccentric and a crowning eccentric link pivotally engaging said crowning eccentric and said lever at a location displaced from the pivoted mounting thereof.

10. The combination of claim 2 characterized in that an elongated rack is mounted adjacent and parallel to said traverse slideway, a traversing crowning pinion is mounted on said traversing carriage for engagernent with said rack, and a gearing train operatively is engaged With said crowning pinion and with said crowning eccentric to rotate the latter and to produce corresponding movements of said crowning link and said carriage section rearward end portion as said traversing carriage is moved along its path of traversing movement.

11. The combination according to claim 7, characterized in that a rack is secured to said supporting link and extended generally along the path of sliding movement thereof and an adjustment shaft is rotatably mounted in said support end portion and terminates in a pinion engaging said rack whereby rotation of said shaft adjustably and slidably positions said supporting link along the lengths of said feed eccentric and said adjustment lever.

12. In a grinding apparatus, the combination comprising an elongated grinding Wheel support, means for pivotally mounting said support, said support being disposed generally normal to a workpiece When supported in said apparatus, means for mounting a grinding Wheel on said support at a location displaced from said pivot mounting means, said pivot mounting means being disposed so that movement of an end portion of said support causes said grinding wheel to be advanced and Withdrawn relative to said workpiece, a crowning eccentric and link Controlled thereby movably mounted adjacent said support end portion, a fine feed eccentric rotatably mounted on said support end portion in engagement with said crowning link so that rotation of said fine feed eccentric produces corresponding movements of said support end portion irrespective of the position of said crowning eccentric 'and link, and means for rotating said fine feed eccentric and said crowning eccentric.

13. The combination according to claim 12 wherein said fine feed eccentric is hollow and said crowning link includes an end portion rotatably mounted in said fine feed eccentric.

References Cited UNITED STATES PATENTS 2,003,883 6/1935 Grundstein 51-165 2,108,310 2/1938 Griffing 51-49 X 2,132,941 10/1938 Flygare 51-49 X 2,254,0=20 8/1941 Schulte et al. 51-165 X 3,070,925 1/ 1963 Woodford et al. 51-49 FOREIGN PATENTS 894,808 4/ 1962 Great Britain.

LESTER M. SWINGLE, Primary Examner. 

